Rotating piston machine having cam controlled alternating pistons

ABSTRACT

A shaft (5) is driven in the rotary piston machine. The torque is transmitted via first cam rings (7), connected to it, to rolling bodies (9) supported in cages and from these rolling bodies to second cam rings (8), which drive the rotation bodies (3) of the rotary piston machine. The cam rings (7, 8) and the rolling bodies (9) are, in this case, partially provided with bevel-wheel teeth and partially with cam track teeth (FIG. 3 ). The rotary piston machine can also be used as an engine and is characterised by a particularly high efficiency.

The invention relates to a rotary piston machine having a casing, havinga shaft supported in the casing, having an annular space in which tworotation bodies are arranged and on whose walls, in which inlet andoutlet openings are provided for the working medium, the rotation bodiesare in sealing contact, each rotation body having sector-shaped paddlesextending radially outwards, the two rotation bodies being coaxiallyarranged and their paddles interleaving with one another in such a waythat each paddle of one rotation body is arranged between two paddles ofthe other rotation body, a cam track control being provided by means ofwhich, on rotation of the shaft, the two rotation bodies executerevolutions with cyclic changes to the rotational velocity and thedistances between the paddles of the two rotation bodies, and the camtrack control has first cam track control means in the form of first camrings, second cam track control means in the form of second cam ringsand third cam track control means in the form of a cage with, heldwithin it so that they cannot be displaced in the peripheral direction,rolling bodies narrowing conically to both ends, which rolling bodiesroll on the first and second cam rings, one of the cam track controlmeans being connected to the shaft and another of the cam track controlmeans being torsionally connected to one of the rotation bodies and theremaining cam track control means being connected to the casing.

In such a rotary piston machine (EP-B1-0 316 346), the cam track controlof the rotation bodies takes place in each case by means of two sets ofelements which each have an inner cam ring, rolling bodies and an outercam ring. Two such sets of controls are necessary because the rollingbodies can only be pressed outwards by the inner cam ring over a certainangular range (e.g. 45°) and these rolling bodies then in turn rotatethe outer cam ring by the outwardly directed force in such a way that atorque can be transmitted from the inner cam ring to the outer cam ring.Subsequently, the rolling bodies must then be moved inwards again;during this time, no torque can be transmitted from the inner cam ringto the outer cam ring. It is therefore necessary to provide a second setof such a cam track control, which effects the torque transmission inthis angular range. The same applies correspondingly, of course, whentorques have to be transmitted from the outer cam ring to the inner camring. It is obvious that the construction is relatively complicated dueto the large number of elements of the cam track control and thatincreased friction losses can also occur. In addition, the cam ringshave a relatively complicated shape so that their manufacture iscomplicated and expensive.

The object of the invention consists in the creation of a rotary pistonmachine, of the type mentioned at the beginning, which is more simplyconstructed.

The solution according to the invention consists in the fact that therolling bodies are provided with bevel-wheel teeth, in the fact that thesurfaces, directed towards the rolling bodies, of the cam tracks of thecam rings are arranged in a rotationally symmetrical area correspondingto the surface of the rolling bodies and are provided with correspondinginternal bevel-wheel teeth, and in the fact that, as a maximum, one camtrack control with a first and a second cam ring and rolling bodies isprovided for each rotation body.

Instead of two of the sets of elements mentioned, only one set remainsnecessary. The rolling bodies no longer transmit the torque from thefirst to the second cam ring, or vice versa, by moving outwards orinwards. Rather, they retain their radial position, at least in themain, and transmit the torques by rotation with the aid of the teeth.

In this case, the rolling bodies roll on the relatively narrow camtracks which protrude from the surfaces of the cam rings directedtowards the rolling bodies. These surfaces are located in areas whichhave substantially the same double-conical shape as the rotation bodiesand are likewise provided with teeth. Such substantially conicalsurfaces can be manufactured far more easily than the complicated camshapes of the previously known rotary piston machine. The surfaces ofthe cam rings directed towards the rolling bodies can also, overall, berotationally symmetrical or double-conical in shape, with the exceptionof the protruding cam tracks, so that they are likewise easier tomanufacture.

Although it is conceivable to provide only one rotation body with a camtrack control, it is expedient to provide one such cam track control foreach of the rotation bodies.

So that the cam track control can operate without clearance, it isexpedient to provide for the teeth to be involute teeth whose involutegeometry is at right angles to the axis of the rolling body.

The advantages of involute teeth are known to the specialist. If theinvolute geometry is at right angles to the axis of the rolling body,and not, as is otherwise usual in the case of bevel-wheel teeth, atright angles to the surface of the cone, there is a profile displacementnear the centre line of the cam track in which the gearwheels stillengage with one another without clearance. This therefore provides ineach case, so to speak, a null transmission on the centre line andV-null transmissions on both sides (Decker, "Maschinenelemente,Gestaltung und Berechnung", Carl Hanser Verlag Munich 1963, pp.370-373).

In involute gears, the engagement angle according to DIN 867 is 20°. Ifprovision is made for the engagement angle to be approximately 30° to50° in particular approximately 35° to 40° it is then possible for thecam rings and rolling bodies to transmit the desired torques and also toaccept radial forces. The cam track controls can therefore act asadditional bearings. Under certain circumstances, it will even bepossible to dispense completely with other bearings, which furthersimplifies the construction of the rotary piston machine.

If the cam rings are built up from two halves arranged axially insequence, they are easier to manufacture. In addition, the cam trackcontrol can be more easily assembled. If the cam rings are clampedtogether axially, which can take place by means of clamping and/or withcorresponding springs, radial forces could act on the bearings of therolling bodies if, for example, the inner cam rings exert a largerradial force than the outer cam rings. It is therefore expedient to makeprovision to ensure that the rolling bodies, which cannot move in theperipheral direction, are held in bearing arrangements which can bedisplaced in the radial direction at least by a certain amount. In thiscase, the rolling bodies can escape from the uneven forces.

It is expedient, in this case, for the rolling body journals in thebearing arrangements to be subjected to an elastic force in thedirection towards the axis of rotation. If no torques are acting, thejournals take up the position adjacent to the axis of rotation withoutclearance. If the torque increases, the journals in the bearingarrangements can give way towards the outside as far as a new limitingposition. In this way, the flank clearance necessary is achieved with aprecisely defined maximum clearance.

In most cases, the intention will be that the rotation bodies should notexecute any net rotational motion relative to one another. For thispurpose, it is expedient to provide for the number of teeth of the innerand outer cam rings to be the same and for this number to be divisibleby the number of paddles. During operation, the central region of therolling body will then interact with the outer cam ring and its endregions will interact with the inner ring.

It is advantageous for each cam track control to have the same number ofrolling bodies as the number of paddles per rotation body.

It is immediately possible to connect the outer cam rings to thecorresponding rotation bodies in such a way that the connection iscompletely present in the part near the axis. The seal surrounding thecorresponding connecting part can therefore likewise be made relativelysmall and does not wear much because relatively small relativevelocities between the rotation and the rotating parts occur here.

The invention is not limited to the cases in which inner and outer camrings are present, as is the case in the prior art (EP-B1-0 316 346). Itis possible to provide, advantageously but not necessarily, for the camrings to be torsionally connected to the shaft and the second cam ringsto be torsionally connected to a rotation body and for the cage to beconnected to the casing. Although, as is the case in the prior art, thefirst cam rings can be arranged radially inwardly of the rolling bodiesand the second cam rings can enclose the first cam rings and the rollingbodies. It is also possible to provide, in accordance with theinvention, for the second cam rings to be arranged radially inwardly ofthe rolling bodies and the first cam rings to enclose the second camrings and the rolling bodies. Because the engagement of the first camrings with the rolling bodies extends over a larger angular range inthis case, the possibly substantial torque can be better transmittedfrom the shaft to the rolling bodies in this way. In addition, thesecond cam rings have a smaller mass and a smaller moment of inertia sothat the mass which has to be repeatedly accelerated and retarded isreduced.

In a further advantageous embodiment, it is possible to provide for thefirst and second cam rings to be arranged adjacent to one anotherradially inside the rolling bodies. In this case also, the forces andtorques can be effectively transmitted because of the teeth, which wouldnot be possible in this embodiment without teeth.

In this case, there is no cam ring outside the rolling bodies. Therolling bodies can, however, be enclosed by a third cam ring of largemass which (with the exception of the guidance by the teeth) is freelyrotatable and can be retarded or accelerated precisely in each caseagainst the acceleration and retardation motions of the rotation bodiesin order, by this means, to ensure smoother running.

If the rolling bodies consist of two parts which can be rotatedindependently of one another, the torque can, in the latter case, beinitially transmitted from the first cam ring to the first part of therolling body and from there to the third cam ring of large mass. Fromthe latter, the torque is then transmitted further via the second partof the rolling body to the second cam ring and from there to therotation body. In this case, a larger number of transmission steps areobtained.

In a further embodiment, it is possible to provide for the first andsecond cam rings to enclose the rolling bodies; both cam rings, whichare arranged adjacent to one another, therefore interact with therolling bodies from the outside.

In another advantageous embodiment, the first cam rings are connected tothe casing, the second cam rings are connected to a rotation body andthe cage is connected to the shaft. In this case, therefore, the torqueis not transmitted from the shaft to the first cam rings but to the cagewhich carries the rolling bodies.

Because the distance between the teeth increases with increasingdiameter in the direction towards the end of the truncated cone,problems can occur at this location. These large distances can beavoided if half of each of the conical surfaces of the rolling bodiesand the cam rings has bevel-wheel teeth and the other half has elevatedcam tracks. The cam track is, so to speak, interrupted and continues,after a certain angular range on one surface, on the other surface ofthe other part.

For even running, it is very important that the teeth and cam tracksshould be configured in such a way that a maximum angular velocity ofone rotation body in each case corresponds to a minimum angular velocityof the other rotation body, that the angular velocity maxima and minimashould be arranged, in each case, at distances apart of half the cycleduration, should have the same values in the centre between two extremevalues, and that the change with time should be a flattened function inthe region of the maxima.

The invention is described below using advantageous embodiments withreference to the enclosed drawings. In these:

FIG. 1 shows a section through a radial plane of the annular space of arotary piston machine of the invention, with the two rotation bodies;

FIG. 2 shows the two rotation bodies in different positions;

FIG. 3 shows one half of the machine in cross-section;

FIG. 4 shows the cam track on the surface of the inner cam ring;

FIG. 5 shows, in section, a somewhat modified embodiment of the rotarypiston machine of FIG. 1;

FIG. 6 shows, in cross-section, another embodiment;

FIG. 7 shows yet another embodiment in section;

FIG. 8 shows a cross-section along the line VIII--VIII of FIG. 7;

FIG. 9 shows, in cross-section, yet another embodiment;

FIG. 10 shows, in cross-section, yet another embodiment;

FIG. 11 shows yet another embodiment in cross-section;

FIG. 12 shows, in axial section, a different type of teeth and camtracks;

FIG. 13 shows a cam ring with the modified teeth and cam track of FIG.12; and

FIG. 14 shows a graphical representation of the change with time of theangular velocity of the cam rings.

The annular space 1 of a rotary piston machine of the invention is shownin FIG. 1 and this annular space 1 is surrounded by parts of the casing2. The two interleaving rotation bodies, which are configured as thepaddle wheels 3 and 4, are located in the annular space 1. The paddlewheel 3 has the paddles 3a, 3b, 3c and 3d, while the paddle wheel 4 hasthe paddles 4a, 4b, 4c and 4d. Both paddle wheels are driven by acentrally arranged shaft 5 in a manner still to be described. Variousinlet openings and outlet openings in the end wall of the annular space1 are indicated by 6a-h.

The mode of operation of this arrangement is as follows. If the shaft 5moves in the anti-clockwise direction, the paddles wheels 3 and 4 arerotated with different velocities in the clockwise direction in a mannerstill to be described. In the position shown, for example,. the paddlewheel 4 would rotate in the clockwise direction more rapidly than thepaddle wheel 3. In this case, the working space between the paddles 3dand 4a would increase so that gas is taken in through the inlet port 6a.At a later time, this inlet port 6a is then closed by the slowlyfollowing paddle 3d. Approximately from this moment onwards, the paddle3d begins to move more rapidly than the paddle 4a, so that the workingspace between the two paddles is reduced and the gas is compressed untilboth paddles have moved sufficiently far that the working space is overthe outlet opening 6b, so that the gas can escape at this point. At thistime, the paddle 3d can be brought up to the paddle 4a so that gas iscompletely expelled at this point.

This mode of operation can be used both for a compressor and for aninternal combustion engine. It would only be necessary to providecombustion spaces, fuel conduits, etc.

Four phases of the working cycle just described are represented in FIG.2. After a 90° rotation of the two rotation bodies, a new working cyclebegins.

An axial section of one half of the machine according to the inventionis represented in FIG. 3. The other half of the machine continues to theleft, essentially as a mirror image.

The drive shaft 5 is rotatably supported in the casing 2 by means of adistance sleeve 15 and journal and thrust bearings 16, 17 and a casingflange 18. Following on outside the distance sleeve 15, there are, inaddition, a coupling flange 19 and a nut 20. The inner cam rings 7consisting of two parts follows inwardly of the distance sleeve 15. Thisis followed on the left by a distance sleeve 21 which leads to thecorresponding inner cam ring 7 on the other end, this other cam ringbeing intended for the drive of the other of the two rotation bodies.

The two halves of the cam inner rings 7 are pressed together via thedistance sleeves 15 and 21 and a corresponding opposing pressure elementon the left-hand side of the machine (not shown) by tightening the nut20 so that the rolling bodies 9 are pressed outwards and, specifically,against the outer cam rings 8. The latter likewise consist of two halvesand are arranged torsionally fixed in an outer sleeve 22 which isconnected to the rotation body 3. The outer cam rings 8 are not onlysecured by means of closing flanges 23 but are also pressed together inorder to create a pressure opposing the pressure of the rolling bodies9. The halves of the inner rings 7 or outer rings 8 can also be pressedtogether by means of spring elements.

Finally, the cage 14, in which the rolling bodies 9 are supported, isfastened to the casing flange 18 and is torsionally connected to thecage on the other end of the arrangement by means of a crown gear 24. Inthis way, the cage is fixed in the peripheral direction relative to thecasing 2. The angular setting of the cage 14 relative to the casing can,however, still be changed by changing the angular setting of the casingflange 18 relative to the casing 2 by means of an adjustment bearing 25.

The rolling bodies 9 are not directly supported in the cage 14 but inbearings 50 of externally cuboid configuration which are accommodated incorresponding grooves of the cage 14 in such a way that they have noclearance in the peripheral direction but can reciprocate a little inthe radial direction. This makes it possible to press the rolling bodies9 outwards on clamping.

In addition, seals are indicated by 26 to 30 and a further seal betweenthe casing halves is indicated by 31. Finally, 32 is a sliding sleevebetween the cage 14 and the rotor 3.

As has been stated, the casing 2 is made up of two halves, the seal 31being provided at the split line 33 of the casing. If the sealing effectbetween the paddles of the rotation bodies 3, 4 and the wall of theannular space 1 deteriorates, it is possible to ensure, by tightening abolt led through the hole 34, that the two casing halves are movedcloser to one another so that there is a better contact between thecasing walls and the rotation bodies 3, 4 in the annular space. Thesealing effect is improved by this means.

The rolling bodies 9 configured in the form of a double cone areprovided with bevel-wheel teeth 51. These are involute teeth, the planeof the involute being at right angles to the journal of the rollingbodies 9. The cam rings 7 and 8 have, on the inside, an area which isessentially similar to the outer surface of the rolling bodies 9. Thereare, however, intermediate spaces 52 between the rings 7, 8, on the onehand, and the rolling body 9, on the other. The rings 7, 8 on the onehand, and the rolling body 9, on the other, are only in contact in theregion of the cam tracks 53 which are provided as elongated protrusionson the inner surface of the cam rings 7, 8. These protrusions carryinvolute teeth on their surface which correspond to those of the rollingbodies 9. The teeth of the rolling bodies 9, as well as those of the camtracks 53 have, like bevel-wheel teeth, a larger module or a largerpitch in the centre than at the axial ends of the rolling body 9. In theperipheral direction, the cam tracks 53 have different distances fromthe central plane. In consequence, the transmission ratio changes--bothfrom the inner cam ring 7 to the rolling body 9 and from the rollingbody 9 to the outer cam ring 8. If the shaft 5 is now driven, the innerring 7 rotates uniformly with it. The rolling body 9 will take up analternating rotational velocity depending on how far, at the moment, thecam track 53 is from the centre line at the contact position between therolling body 9 and the inner ring 7. The transmission ratio between therolling body 9 and the outer ring also varies correspondingly so thatthe rotation body 3 executes the desired, non-uniform rotary motion.

The embodiment of FIG. 3 has four rolling bodies 9, of which two arevisible in the figure. Two further rolling bodies 9 are located at anangular distance of 90° in front of the plane of the drawing and behindthe plane of the drawing. The cam tracks 53 have, in this case, a curve(distance from the central plane as a function of the angle about thecentral axis of the rolling body) which has a period of 90°.

The curve track of the outer surface of a half of an inner cam ring 7 isshown in FIG. 4. The cam track 53 has, as may be clearly seen, adistance from the central plane which varies with angle. The involuteteeth 54 have a larger module (pitch, distance between teeth) near thecentre line (at B) than they have in the outer region (at A).

Only the surroundings of a rolling body 9 are represented in each of theFIGS. 5 to 11 in order to make clear the mode of operation of otherembodiments. In contrast to FIG. 1, the relationships to the left of thecentral plane of the machine are represented in this case.

The embodiment of FIG. 5 corresponds essentially to the embodiment ofFIG. 3. The only point here is that the outer cam ring 8 is notconnected to the rotation body 4 near its periphery but near the shaft5. The casing 2 therefore only requires a relatively small hole throughwhich the second cam ring 8 and the rotation body 4 are connected at theperiphery of the shaft 5. Only relatively slight relative peripheralvelocities occur, therefore, in the region of a seal 55 arranged here sothat the wear on the seal is less.

In the embodiment of FIG. 6, the first cam ring 7, which is directlyconnected to the shaft 5, is arranged outside the rolling bodies 9. Thisprovides better engagement between the two parts and permits a bettertransmission of the torque to the rolling bodies 9. The second cam ring8 is arranged within the rolling bodies 9 and is again connected to therotation body 4. The advantage is that the non-uniformly moved mass issmaller than in the case of the first embodiment.

In the embodiment of FIG. 7, the first cam ring 7 is arranged adjacentto the second cam ring 8; both cam rings are arranged within the rollingbody 9. The first cam ring 7 is torsionally connected to the shaft 5 andthe second cam ring 8 is torsionally connected to the rotation body 4.The torque transmission takes place without an outer cam ring. In thiscase, however, a cam ring 64 which can be freely rotated, apart from theteeth, is provided. This cam ring 64 is moved and accelerated ordecelerated oppositely to the rotation body 4 so that the machine runsmore evenly.

It may also be seen in the figure that the rotary body 9 is built upfrom two parts and is supported by means of a step-shaped bearing 56 ona central shaft 57. The central shaft 57 is supported in cuboid bearings50 which cannot move in the peripheral direction but can move outwards alittle in the radial direction against the force of a spring 58. If notorques are transmitted, the bearings 50 are in the radially innerposition and are then pressed outwards in the case of larger torquesagainst the force of the spring or springs 58, limits being set to thisoutwardly directed motion. The bearings 50, the shaft 57 of the rotationbodies and the spring 58 are represented even more clearly in FIG. 8.The stop surface 59, which limits the radially outward motion of thebearing part 50 may also be recognised in this figure.

In the embodiment of FIG. 9, the rolling body consists of two parts 9aand 9b between which bearings 60 are arranged. The torque is transmittedfrom the shaft to the first cam ring 7, from there to the left-handrolling body part 9a and from there to the outer cam ring 64 of largemass, which again acts against torque fluctuations and rotationalaccelerations of the rotation body 4 or compensates for them. Thetransmission of the torque then takes place from the cam ring 64 oflarge mass to the right-hand part 9b of the rolling body and from thereto the inner second cam ring 8, which is again connected to the rotationbody 4. There is a double transmission ratio in this case.

In the embodiment of FIG. 10, both the first cam ring 7 and the secondcam ring 8 engage externally on the rolling body 9. This provides a morereliable torque transmission from the cam rings to the rolling body andvice versa, because the rolling body 9 fits into corresponding curvedareas of the cam rings 7 and 8 whereas, in the case of an inner camring, the contact which takes place is more or less only point contact.The first cam ring 7 is rotationally connected to the shaft 5 and thesecond cam ring 8 to the rotation body 4.

In the embodiment of FIG. 11, the first cam ring 7 is connected to thecasing 2. The torque from the shaft 5 is transmitted to the cage 14connected to it, this cage 14 rotating with the shaft 5. The torque isthen transmitted via the freely rotating rolling body 9 to the secondcam ring 8 which is in turn connected to the rotation body 4.

In the embodiment of FIG. 12 and 13, the inner ring (only one inner ringhalf is shown), for example the inner ring 7 of the embodiment of FIG. 1to 4, is provided as shown in FIG. 13, with bevel-wheel teeth 54 in theapex part and with cam track teeth 53 in the part located furthertowards the end of the truncated cone. This avoids the teeth having verylarge distances apart at the end of the truncated cone.

The rolling body 9 or the rolling body half 9, which is represented inFIG. 12, is configured in an exactly complementary manner. Theinterrupted cam tracks 53 are continued in an analogous manner in therespectively other part.

It may be seen from the diagram of FIG. 14 that during the course of acycle (0-1 on the t axis), the angular velocity of the two cam rings 8in each case moves from a minimum value to a maximum value and then backto a minimum value. After half a period in each case, the minimum valueof one cam ring has changed to the maximum value and vice versa. Bothreach the half value precisely in the centre between the maximum valuesin each case. In the region of the maxima and minima, the curves are notpeaked but are flattened so that a larger period is available here forgas exchange.

I claim:
 1. Rotary piston machine having a casing (2), having a shaft(5) supported in the casing (2), having an annular space (1) in whichtwo rotation bodies (3, 4) are arranged and on whose walls, in whichinlet and outlet openings (6a-6h) are provided for the working medium,the rotation bodies (3, 4) are in sealing contact, each rotation body(3, 4) having sector-shaped paddles (3a-3d, 4a-4d) extending radiallyoutwards, the two rotation bodies (3, 4) being coaxially arranged andtheir paddles interleaving with one another in such a way that eachpaddle of one rotation body is arranged between two paddles of the otherrotation body, a cam track control (7, 8, 9) being provided by means ofwhich, on rotation of the shaft (5), the two rotation bodies (3, 4)execute revolutions with cyclic changes to the rotational velocity andthe distances between the paddles of the two rotation bodies, and thecam track control has first cam track control means in the form of firstcam rings (7), second cam track control means in the form of second camrings (8) and third cam track control means in the form of a cage (14)with, held within it so that they cannot be displaced in the peripheraldirection, rolling bodies (9) narrowing conically to both ends, whichrolling bodies (9) roll on the first (7) and second (8) cam rings, one(7, 8, 14) of the cam track control means being connected to the shaft(5) and another (7, 8, 14) of the cam track control means beingtorsionally connected to one of the rotation bodies (3, 4) and theremaining cam track control means (7, 8, 14) being connected to thecasing (2), characterised in that the rolling bodies (9) are providedwith bevel-wheel teeth (51), in that the surfaces, directed towards therolling bodies (9), of the cam tracks (53) of the cam rings (7, 8) arearranged in a rotationally symmetrical area corresponding to the surfaceof the rolling bodies (9) and are provided with correspondingbevel-wheel teeth (54), and in that, as a maximum, one cam track controlwith a first and a second cam ring (7, 8) and rolling bodies (9) isprovided for each rotation body (3, 4).
 2. Rotary piston machineaccording to claim 1, characterised in that one cam track control (7, 8,9, 51, 52) is provided for each rotation body (3, 4).
 3. Rotary pistonmachine according to claim 1, characterised in that the cam rings (7, 8)are substantially rotationally symmetrical with the exception of the camtracks (53).
 4. Rotary piston machine according to claim 1,characterised in that the teeth (51, 54) are involute teeth whoseinvolute geometry is at right angles to the axis of the rolling body(9).
 5. Rotary piston machine according to claim 1, characterised inthat the cam rings (7, 8) are built up from two axially sequentialhalves.
 6. Rotary piston machine according to claim 5, characterised inthat the rolling bodies (9) are held in bearing arrangements (50) whichcan be displaced in the radial direction.
 7. Rotary piston machineaccording to claim 6, characterised in that the journals of the rollingbodies (9) in the bearing arrangements (50) are subjected to an elasticforce in the direction towards the axis of rotation.
 8. Rotary pistonmachine according to claim 7, characterised in that the elastic force isa spring force, a gas pressure or a hydraulic pressure.
 9. Rotary pistonmachine according to claim 1, characterised in that the number of teethof the inner and outer cam rings (7, 8) is the same and is divisible bythe number of paddles (3a, 3b, 3c, 3d).
 10. Rotary piston machineaccording to claim 1, characterised in that the number of rolling bodies( 9 ) of each cam track control ( 7, 8, 9, 51, 52) is divisible by thenumber of paddles of the rotation body (3, 4).
 11. Rotary piston machineaccording to claim 1, characterised in that the first cam rings (7) aretorsionally connected to the shaft (5) and the second cam rings (8) aretorsionally connected to a rotation body (3, 4) and the cage (14) isconnected to the casing.
 12. Rotary piston machine according to claim11, characterised in that the first cam rings (7) are arranged radiallyinwardly of the rolling bodies (9) and the second cam rings (8) enclosethe first cam rings (7) and the rolling bodies (9).
 13. Rotary pistonmachine according to claim 11, characterised in that the second camrings (8) are arranged radially inwardly of the rolling bodies (9) andthe first cam rings (7) enclose the second cam rings (8) and the rollingbodies (9).
 14. Rotary piston machine according to claim 11,characterised in that the first (7) and second (8) cam rings arearranged adjacent to one another radially inwardly of the rolling bodies(9).
 15. Rotary piston machine according to claim 14, characterised inthat the rolling bodies are enclosed by a third cam ring (64) of largemass.
 16. Rotary piston machine according to claim 15, characterised inthat the rolling bodies (9) consist of two parts (9a, 9b) which can berotated independently of one another.
 17. Rotary piston machineaccording to claim 11, characterised in that the first (7) and second(8) cam rings enclose the rolling bodies (9).
 18. Rotary piston machineaccording to claim 1, characterised in that the first cam rings (7) areconnected to the casing, the second cam rings (8) are connected to arotation body (3, 4) and the cage (14) is connected to the shaft (5).19. Rotary piston machine according to claim 1 characterised in thathalf of each of the conical surfaces of the rolling bodies (9) and ofthe cam rings (7, 8, 64) has bevel-wheel teeth (54) and the other halfhas elevated cam tracks (53).
 20. Rotary piston machine according toclaim 1, characterised in that the teeth (54) and the cam tracks (53)are configured in such a way that a maximum angular velocity of onerotation body (3, 4) in each case corresponds to a minimum angularvelocity of the other rotation body (4, 3), in that the angular velocitymaxima and minima are arranged, in each case, at distances apart of halfthe cycle duration, have the same values in the centre between twoextreme values, and in that the change with time is a flattened functionin the region of the maxima.